High speed double blow header



Nov. 21, 1967 NEBENDORF ET AL HIGH SPEED DOUBLE BLOW HEADER 4 Sheets-Sheet 1 Filed March 29, 1965 ,'I,\ u n 1,1111% 'IIIIIIIIIIII/IZ-INVENTOR: W 16i; I

H. NEBENDORF ET AL 3,353,417

HIGH SPEED DOUBLE BLOW HEADER Nov. 21, 1967 4 Sheets-Sheet 2 Filed March29, 1965 INVENTORS Nov. 21, 1967 H. NEBENDORF ET AL 3,353,417

HIGH SPEED DOUBLE BLOW HE'ADER 4 Sheets-Sheet '5 Filed March 29, 1965INVENTORS Nov. 21, 1967 H- NE BENDORF ET AL 3,353,411

HIGH SPEED DOUBLE BLOW HEADER Filed March 29, 1965 4 Sheets-Sheet 4INVENTORS Z United States Patent Ofitice 3,353,417 Patented Nov. 21,1967 many Filed Mar. 29, 1965, Ser. No. 443,385 Claims priority,applicatgtgnggsermany, Oct. 8, 1964,

2 Claims. (2174-53 The present invention relates to high speed doubleblow headers. Double blow headers are known which have a bed framedisclosed in Patent No. 3,031,698. The bed frame carries a reciprocatingheader slide, or gate, driven by a crank-shaft on the frame, which gatecarries a shiftable punch carrier operated at half crankshaft speed, sothat on one advance stroke of the gate a first punch or tool engages ablank held by transfer fingers in alignment with a die, pushes the blankinto the die and upsets the blank, and on the next advance stroke thepunch carrier has shifted and so presents a second punch or tool to thework now recessed in the same die. After the second blow the blank isejected from the die and the transfer fingers bring a new blank into aprojected position in front of the die.

In these headers, the main or driving crankshaft turns continuously, asdoes the half speed cam shaft. This means that the gate, carrying thepunches or tools is ever moving except at the very end of its stroke.The punch carrier, however, must remain motionless relative to the gateduring the final portion of each advance stroke of the gate, while apunch is upsetting a blank in the die. The problem is one of moving thepunch carrier mounted on the gate so as to shift the carrier between itstwo alternative positions at the correct time, and of positivelymaintaining the carrier in its operating position during the finalportion of each advance stroke of the gate.

Reliance on a combination of positive stops for the punch carriercoupled with spring over-travel accommodation devices is unsatisfactory,particularly at high speed operation, because of flutter, bounce,pounding and general unreliability or inconsistency in operation. All ofthese occurrences can result in misalignment of the punches or toolswith the work or die, and thus break or injure expensive tool parts.

The speed of operation of the machine, and the durability of the partsin service, also depend upon the necessary rates of acceleration anddeceleration, and upon the mass of the parts which must be soaccelerated and decelerated, since excessive loads on the driving andbearing parts cause excessive wear or breakage, and also interfere withthe desired accuracy of timing and positioning, because of compressionand stretch of the parts.

Accuracy is combined with maximum speed of operation in a double blowheader by mounting on the reciprocating slide or gate a shiftable punchcarrier, and an oscillating, positive motion cam means for shifting thecarrier while controlling its acceleration and deceleration, and yetpositively holding the carrier in its two operating positions. The cammeans is oscillated by connections driven by the crankshaft, and themotion imparted to such connections by the reciprocation of the gaterelative to the frame is accommodated by relatively small movement ofthe cam means on the gate in either direction, without correspondingmovement of the punch carrier after it has moved the cam means on thegate to either of its two operating positions. In this manner thecritical part of the movement of each of the parts on the gate isminimized, thereby minimizing the necessary rate of acceleration anddeceleration and permitting the punch carrier to be moved to, andpositively held in, each of its operating positions with maximum speedof operation followed by accuracy of positioning. This arrangement alsominimizes the mass of the parts which must be carried on thereciprocating gate, thereby further contributing to speed andreliability of operation.

The positive motion cam means carried by the reciprocating gate isoscillated by a second positive motion cam means on the frame, thelatter cam means being driven by a continuously rotating half speedshaft geared to the crankshaft. This arrangement takes advantage of allof the advantages of the oscillating positive motion cam means carriedon the gate and, at the same time, permits the second cam means on theframe to be contoured to give the optimum rate of acceleration anddeceleration in each direction. It is necessary for the first punch tobe shifted into, and held in alignment with, the die at a pointsubstantially before the end of the first stroke of the gate so that thepunch may engage a new blank held in transfer fingers, push the blankdown into the die and finally upset the projecting end of the blank.However, the shifting movement to bring the second punch into alignmentwith the die can start at a point wherein the gate is much closer to theface of the die and such shifting motion can continue through theremainder of the first retracting stroke and the greater portion of thesecond advancing stroke, since the blank now remains seated andretracted in the die. Similarly, the carrier can start the shiftingmovement to bring the firts punch back into alignment with the die at apoint very close to the face of the die after the second blow but mustcomplete this shifting movement at a point wherein the gate is spacedmuch farther back from the die on the next advance stroke so as to allowthe necessary travel to push the next new blank into the die. Any extradwell of either punch which may be required by a long punch or by aknock-out operation working on a long blank, in either the first or thesecond punch can be accommodated, all while maintaining optimum rates ofacceleration and deceleration at all other points in the cycle.

The motion of the cam means on the frame is transmitted to theoscillating cam means on the reciprocating gate by a connecting rodhaving ball and socket or universal joint connections permitting thereciprocation of the gate during the transmission of the oscillatingmotion between the two cam means. The use of a connecting rod forcoupling the two cam means eliminates sliding connections between theparts. Such sliding connections are subject to inaccuracy frommanufacturing tolerances and wear, and also from springing or yieldingunderacceleration and deceleration loads.

It is one object of the present invention to provide a high speed doubleblow header, wherein very precise end positions of the first and secondpunches or tools, determined by cams, are obtained forcibly andplay-free without any particular abutments, to reduce thereby thereciprocating masses, in order to obtain an appreciable increase of thenumber of revolutions of the shaft, to avoid wear and to obtain,nevertheless, advantageous extended resting periods during the blowheader operation.

It is another object of the present invention to provide a high speeddouble blow header, wherein the axle of the shiftable punch carrier isoperated by means of a directly forced cam drive.

It is still another object of the present invention to provide a highspeed double blow header, wherein the swinging axle of the pair ofangular arms carrying follower-rollers constitutes simultaneously theswinging axis of the shiftable punch carrier formed as swinging wing.

By this arrangement a precise transmission of the cam strokes istransmitted directly to the shiftable punch carrier, without loss andfree of error. The transmission of the driving rotary forces is therebyfavorable and reliable as well as easily obtained in exact synchronism.No wear occurs during long time operation, and thus an adjustment isintentionally omitted. The exact forced operation makes possible in anadvantageous manner, during the press operation longer resting periodsfor the purpose of an equalized forming of the work piece.

In order to advantageously leave the shiftable punch carrier in one endposition appreciably longer than in the other end position, cams arerequired which are disposed symmetrically. A forced roller guide isobtained, in accordance with the present invention, such, that the pathsof the cams disposed in adjacent planes are formed of the same size, aswell as set off relative to each other in relation to a symmetry planewith its equally formed control profiles, so that the follower-rollersitting on the angular pair of arms is engaged at each point of the camposition free of play.

A simple structure of reliable operation is obtained, in accordance withthe present invention, such, that the cams coordinated to the pair ofangular arms sit on a profiled shaft, which is driven by means of a pairof bevelled gears immovably mounted on the machine frame, and one of thebevelled gears is mounted displaceably on the profile key shaft.

The same arrangement lends itself also for a linearly moveable punch ortool carrier, without causing disadvantageous effects. In accordancewith the present invention, for this purpose, a slide-like guided toolcarrier is pivotally connected with one of the arms by means of a slidemounted in the punch or tool carrier.

With these and other objects in view, which will become apparent in thefollowing detailed description, the present invention will be clearlyunderstood in connection with the accompanying drawings, in which:

FIG. 1 is a longitudinal section of the device designed in accordancewith the present invention with the swinging tool carrier;

FIG. 2 is an end view of the control drive seen in the direction of thearrow X of FIG. 1;

FIG. 3 is an elevation of one of the cams;

FIG. 4 is a perspective front elevation of the drive shownin FIG. 2;

FIG. 5 is a longitudinal section of the device with a slide-likedisplaceable tool carrier;

FIG. 6 is an elevation of the control drive seen in the direction of thearrow Y of FIG. 5; and

FIG. 7 is a perspective view of the control drive disclosed in FIG. 6.

Referring now to the drawings, and in particular to the embodimentdisclosed in FIGS. 1-4, a press slide 1 is guided in a machine frame(not shown), which press slide 1 is driven to perform a reciprocatingmovement by a connecting rod 2, substantially as disclosed in Patent No.1,918,910 to Hilgeland.

A punch or tool carrier 3, reciprocating within the cycle is mountedcrosswise at the end face of the press slide 1, which tool carrier 3carries the tools and dies 4 and 5.

Thus the punch transfer mechanism comprises a bevel gear 16 on thehalf-speed, or secondary shaft 16 driving a mating bevel gear on thehollow shaft 15 which rotates. In the hollow shaft 15' is mounted afemale spline. A second shaft 14 aligned with the hollow shaft 15 iscarried in bearings on the slide 1 of the header. At one end of theshaft 14, a male spline engages the aforementioned female spline. At theother end of the shaft 14 are mounted a pair of complementary earns 11and 12 which are keyed to and driven by the shaft 14. The cams 11 and 12provide motion to the punch carrier plate 3 and to substantially definethe end points of its travel. The cam shaft 14 makes one complete turnin the exact same time interval required for the header slide on whichit is mounted to make two complete reciprocating strokes.

The tool carrier 3 is swingably mounted with an axle 6. A pair ofangular arms is keyed to the axle 6, the arms 7 and 8 of the pair beingdisposed in opposite directions and in series relative to thelongitudinal direction of the swinging axle 6 in adjacent planes. Theyconsitiute a double lever operating like a seesaw.

Each of the arms 7 and 8 is equipped at its end with cam-followerrollers 9 and 10, respectively. The swinging axle 6 of the angular pairof arms 8 and 9 carrying the cam-follower rollers 9 and 10 issimultaneously the swinging axis of the tool carrier 3 on which thetools 4 and 5 are mounted. The roller 10 engages a cam 11, while theroller 9 engages a second cam 12.

The two cams 11 and 12 cooperating with the rollers 9 and 10 aredisposed in parallel planes and are mounted on a common hub 13, which iskeyed to the shaft 14 mounted below the press slide 1.

The shaft 14 is driven by means of bevelled gears 15 and 16 mounted forrotation in a machine frame (not shown). The earns 11 and 12 are set offrelative to each other, so that upon reaching the highest point of thecam 11 by the roller 10, the roller 9 has reached about the lowermostpoint of the cam 12.

By this arrangement a completely forced and tolerancefree engagement ofthe rollers 9 and 10 on the cams 11 and 12 is brought about, and wherebya satisfactory end position of the tool carrier 3 is obtained.

Referring now again to the drawings, and in particular to FIGS. 57,which disclose a second embodiment of the present invention, a toolcarrier 17 guided along a straight line slide-like in the press slide 1is provided, which tool carrier 17 carries the tools 4' and 5'.

Here again a swinging axle 6 is provided similarly to the arrangement inthe first embodiment and forms the swinging axis for the arms, the arms7' and 8 are keyed in series arrangement in the same manner as disclosedin connection with the first embodiment. The arms 7 and 8' are equippedagain with rollers 9 and 10'. The roller 9' engages a cam 12 and theroller 10' engages a cam 11'. Both earns 11' and 12' are keyed to acommon hub 13', which is keyed to the profiled splined shaft 14' in thesame manner as disclosed in connection with the first describedembodiment.

Contrary to the embodiment disclosed in FIGS. 1-4, the arm 7' is,however, pivotally conected with the longitudinally displaceable toolcarrier 17, and in particular by means of a pin 19 which is mounted on aslide 19' guided in a slot 18 of the tool carrier 17. The pin 19 ispivotally connected with the arm 7'.

Thus, in the second embodiment two earns 11' and 12' are again providedwhich are disposed in series and each of which engages a roller 9 and10', respectively, which are rotatably mounted on the arms 7' and 8'swingable about the swinging axle 6.

For assuring the end positions of the tool carrier 17, a locking device20 is also provided in both embodiments of the present invention, whichlocking device slidingly locks the tool carrier 3.

While we have disclosed two embodiments of the present invention, it isto be understood that these embodiments are given by example only andnot in a limiting sense, the scope of the present invention beingdetermined by the objects and the claims.

We claim:

1. In a header,

a press slide mounted for reciprocating movement,

a punch carrier,

means mounting said punch carrier on said press slide for angularoscillating motion between two alternative work positions,

first cam means rotatably mounted on said press slide and having liftportions and dwell portions,

a first follower on said punch carrier and constantly in engagement withsaid first cam means,

second cam means rotatably mounted on said press I slide and having liftportions and dwell portions,

a second follower on said punch carrier and constantly in engagementwith said second cam means,

a shaft rotatably mounted below said press slide and rotating in timedrelation to the reciprocation of said press slide,

said first cam means and said second cam means continuously rotated bysaid shaft and shifting said punch carrier during their rotation betweensaid two alternative work positions by direct engagement with said firstand second followers, respectively,

an axle fixed to said punch carrier,

said followers comprising oppositely disposed arms secured to said axle,

each of said arms carrying a follower roller, and

said first and second cam means rotating in parallel planesperpendicularly to the axis of said shaft and spaced apart at a distanceequal to the distance of said arms along the axis of said shaft.

2. In a header,

a press slide mounted for reciprocating movement,

a punch carrier,

means mounting said punch carrier on said press slide for linearreciprocating movement between two alternative work positions,

first cam means rotatably mounted on said press slide and having liftportions and dwell portions,

a first follower on said punch carrier and constantly in engagement withsaid first cam means,

second cam means mounted on said press slide and having lift portionsand dwell portions,

a second follower on said punch carrier and constantly in engagementwith said second cam means,

a shaft rotatably mounted below said press slide and rotating in timedrelation to the reciprocation of said press slide,

said first cam means and said second cam means continuously rotated bysaid shaft and reciprocating said punch carrier during their rotationbetween said two alternative work positions by direct engagement withsaid first and second followers, respective,

an axle pivotally mounted in said press slide,

said followers comprising oppositely disposed arms secured to said axle,

each of said arms carrying a follower roller,

said first and second cam means rotating in parallel planesperpendicular to the axis of said shaft and spaced apart at a distanceequal to the distance of said arms along the axis of said shaft,

said punch carrier having a slot,

a slide guided in said slot for lateral movement in said punch carrier,and

a pin pivotally connected with said slide and pivotally connected withone of said arms.

References Cited UNITED STATES PATENTS 651,828 6/1900 Copland 74-541,918,910 7/ 1933 Hilgeland. 2,427,395 9/ 1947 Kellogg 7454 X 2,599,0536/1952 Friedman 1012.5 2,830,456 4/ 1958 Stafford 74--53 MILTON KAUFMAN,Primary Examiner.

D. H. THIEL, Assistant Examiner.

2. IN A HEADER; A PRESS SLIDE MOUNTED FOR RECIPROCATING MOVEMENT, APUNCH CARRIER, MEANS MOUNTING SAID PUNCH CARRIER ON SAID PRESS SLIDE FORLINEAR RECIPROCATING MOVEMENT BETWEEN TWO ALTERNATIVE WORK POSITIONS,FIRST CAM MEANS ROTATABLY MOUNTED ON SAID PRESS SLIDE AND HAVING LIFTPORTIONS AND DWELL PORTIONS, A FIRST FOLLOWER ON SAID PUNCH CARRIER ANDCONSTANTLY IN ENGAGEMENT WITH SAID FIRST CAM MEANS, SECOND CAM MEANSMOUNTED ON SAID PRESS SLIDE AND HAVING LIFT PORTIONS AND DWELL PORTIONS,A SECOND FOLLOWER ON SAID PUNCH CARRIER AND CONSTANTLY IN ENGAGEMENTWITH SAID SECOND CAM MEANS, A SHAFT ROTATABLY MOUNTED BELOW SAID PRESSSLIDE AND ROTATING IN TIMED RELATION TO THE RECIPROCATION OF SAID PRESSSLIDE, SAID FIRST CAM MEANS AND SAID SECOND CAM MEANS CONTINOUSLYROTATED BY SAID SHAFT AND RECIPROCATING SAID PUNCH CARRIER DURING THEIRROTATION BETWEEN SAID TWO ALTERNATIVE WORK POSITIONS BY DIRECTENGAGEMENT WITH SAID FIRST AND SECOND FOLLOWERS, RESPECTIVE, AN AXLEPIVOTALLY MOUNTED IN SAID PRESS SLIDE, SAID FOLLOWERS COMPRISINGOPPOSITELY DISPOSED ARMS SECURED TO SAID AXLE, EACH OF SAID ARMSCARRYING A FOLLOWER ROLLER, SAID FIRST AND SECOND CAM MEANS ROTATING INPARALLEL PLANES PERPENDICULAR TO THE AXIS OF SAID SHAFT AND SPACED APARTAT A DISTANCE EQUAL TO THE DISTANCE OF SAID ARMS ALONG THE AXIS OF SAIDSHAFT,